US4712660A - Electromotive variable-speed and control drive particularly for use in industrial sewing machines - Google Patents

Electromotive variable-speed and control drive particularly for use in industrial sewing machines Download PDF

Info

Publication number
US4712660A
US4712660A US06/836,328 US83632886A US4712660A US 4712660 A US4712660 A US 4712660A US 83632886 A US83632886 A US 83632886A US 4712660 A US4712660 A US 4712660A
Authority
US
United States
Prior art keywords
brake
cooling
flywheel
clutch
bearing bracket
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Fee Related
Application number
US06/836,328
Other languages
English (en)
Inventor
Hans Erndt
Erich Link
Adolf Martin
Herbert Palloch
Hilmar Wittler
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Frankl and Kirchner GmbH and Co KG
Original Assignee
Frankl and Kirchner GmbH and Co KG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Frankl and Kirchner GmbH and Co KG filed Critical Frankl and Kirchner GmbH and Co KG
Assigned to FRANKL & KIRCHNER GMBH & CO KG FABRIK FUR ELEKTROMOTOREN U. ELEKTRISCHE APPARATE reassignment FRANKL & KIRCHNER GMBH & CO KG FABRIK FUR ELEKTROMOTOREN U. ELEKTRISCHE APPARATE ASSIGNMENT OF ASSIGNORS INTEREST. Assignors: PALLOCH, HERBERT, ERNDT, HANS, LINK, ERICH, MARTIN, ADOLF, WITTLER, HILMAR
Application granted granted Critical
Publication of US4712660A publication Critical patent/US4712660A/en
Anticipated expiration legal-status Critical
Expired - Fee Related legal-status Critical Current

Links

Images

Classifications

    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02K—DYNAMO-ELECTRIC MACHINES
    • H02K7/00—Arrangements for handling mechanical energy structurally associated with dynamo-electric machines, e.g. structural association with mechanical driving motors or auxiliary dynamo-electric machines
    • H02K7/10—Structural association with clutches, brakes, gears, pulleys or mechanical starters
    • H02K7/112—Structural association with clutches, brakes, gears, pulleys or mechanical starters with friction clutches in combination with brakes
    • D—TEXTILES; PAPER
    • D05—SEWING; EMBROIDERING; TUFTING
    • D05B—SEWING
    • D05B69/00—Driving-gear; Control devices
    • D05B69/10—Electrical or electromagnetic drives
    • D05B69/12—Electrical or electromagnetic drives using rotary electric motors
    • D05B69/125—Arrangement of clutch-brake construction
    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02K—DYNAMO-ELECTRIC MACHINES
    • H02K7/00—Arrangements for handling mechanical energy structurally associated with dynamo-electric machines, e.g. structural association with mechanical driving motors or auxiliary dynamo-electric machines
    • H02K7/02—Additional mass for increasing inertia, e.g. flywheels
    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02K—DYNAMO-ELECTRIC MACHINES
    • H02K7/00—Arrangements for handling mechanical energy structurally associated with dynamo-electric machines, e.g. structural association with mechanical driving motors or auxiliary dynamo-electric machines
    • H02K7/10—Structural association with clutches, brakes, gears, pulleys or mechanical starters
    • H02K7/112—Structural association with clutches, brakes, gears, pulleys or mechanical starters with friction clutches in combination with brakes
    • H02K7/1125—Magnetically influenced friction clutches and brakes
    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02K—DYNAMO-ELECTRIC MACHINES
    • H02K9/00—Arrangements for cooling or ventilating
    • H02K9/02—Arrangements for cooling or ventilating by ambient air flowing through the machine
    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02K—DYNAMO-ELECTRIC MACHINES
    • H02K9/00—Arrangements for cooling or ventilating
    • H02K9/14—Arrangements for cooling or ventilating wherein gaseous cooling medium circulates between the machine casing and a surrounding mantle
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
    • Y02E60/00—Enabling technologies; Technologies with a potential or indirect contribution to GHG emissions mitigation
    • Y02E60/16—Mechanical energy storage, e.g. flywheels or pressurised fluids

Definitions

  • This invention relates to an electromotive variable-speed and control drive particularly for use in industrial sewing machines.
  • a drive of this type known from U.S. Pat. No. 4,556,132 exhibits an annular cylindrical cooling channel, positioned around the stator frame, through which the air is sucked by the disk flywheel in the form of a fan.
  • the radial outer area of the disk flywheel exhibits channels through which the air is sucked or pushed by the reason of the disk flywheel turning.
  • the air exits in an approximately axial direction and flows between the cooling ribs attached to the outer perimeter of the brake end shield. This does not guarantee satisfactory cooling in particular of the thermally highly-stressed disk flywheel.
  • An object of the invention is to provide a variable-speed and control drive particularly for use in industrial sewing machines which assures a satisfactory cooling of both motor and the coupling and brake unit.
  • the cooling air is released to the cooling air from the cooling ribs attached to the stator frame so that the warming of the shell--something which the seamstress finds particularly unpleasant--is greatly reduced. Since the air flows in an extensively straight line in the cooling channels confined by the ribs, only slight turbulence and thus an only slight resultant noise development results. Since the suction area of the fan in the form of an axial-radial blower extends to the proximity of the coupling surface particularly intensive cooling in this critical area is assured.
  • the invention provides that a sufficient suction power of the fan is attained and, at the same time, that the cooling air is admitted to a very large part of the radial span of the thermally highly-stressed disk flywheel.
  • the radial channels providing a high suction power and a high cooling power are realized in a constructively simple manner.
  • the invention provides that the air exiting from the radial channels formed on the disk flywheel is redirected into a current which intensively cools the outer perimeter of the brake end shield.
  • the cooling of the brake end shield is additionally intensified.
  • the invention also provides that the front side of the brake end shield is subject to particularly intensive cooling while also facilitating the prior exit of a part of the heated air possibly carrying fluff which has been sucked through the air channels.
  • the invention facilitates, as with the disk flywheel, the transport of the cooling air at the brake end shield to the proximity of the thermally highly-stressed brake area.
  • the invention facilitates the releasing of heat produced from the coupling coil or the brake coil to the cooling air along a very direct path.
  • the invention further minimizes the degree of heat given off to the shell surrounding the stator frame.
  • the drive also includes a drive shaft.
  • the clutch-brake unit comprises a clutch-brake disk which is connected to the drive shaft non-rotatably with respect thereto.
  • the clutch-brake unit also comprises a non-rotatable brake bearing bracket having a brake surface.
  • the clutch-brake disk is capable of being brought into friction engagement optionally with the brake surface of the brake bearing bracket or optionally with the clutch surface of the flywheel.
  • the motor has a stator frame and an outer shell confining a cooling region surrounding the stator frame.
  • the flywheel forms a fan sucking cooling air. Cooling channels confined by cooling ribs are provided at the stator frame and the fan is in the form of an axial-radial blower having a suction region extending close to the clutch surface.
  • FIG. 1 shows an axial longitudinal section of a drive according to the invention comprising a motor and brake-coupling unit
  • FIG. 2 shows the brake-coupling unit from FIG. 1 to an enlarged scale
  • FIG. 3 shows a partial cut-out from the brake-coupling unit
  • FIG. 4 shows another partial cut-out from the brake-coupling unit.
  • the drive represented in the drawings comprises a motor 1 and a brake-coupling unit 1.
  • the motor 2 preferably comprises a substantially cylindrical stator frame 3 in which a stator comprising stator windings 4 and a stator bundle of laminations 5 is positioned concentrically in the usual way.
  • a rotor 7 is also positioned concentrically to the central longitudinal axis 6. This rotor is attached to a motor shaft 8.
  • the motor shaft 8 is run on bearings in end shields 9, 10.
  • the end shield 10 positioned away from the brake-coupling unit 2 (brake-clutch unit) preferably is cast in one piece with the stator frame 3.
  • the motor shaft is run on bearings in the bearing bore hole 11 preferably by means of a rolling bearing 12 which is a radial-axial ball bearing.
  • the inner ring 13 of the rolling bearing 12 is supported against a collar 14 of the motor shaft 8.
  • the outer ring 15 of the rolling bearing 12 is supported via a pretensioned screw pressure spring 16 against a stop ring 17 which preferably is formed in one piece with the end shield 10 so that, on the one hand, it is assured that the rolling bearing 12 will not travel axially on the motor shaft 8 and, on the other hand, that axial adjustments of the motor shaft 8 within the play of the spring 16 are possible.
  • the end shield 9 preferably is formed in one piece with an approximately cylindrical casing 18 and screw-connected (20) via centering pins 19 to the stator frame 3 concentrically to the axis 6.
  • the motor shaft 8 preferably is also supported in the bearing bore hole 21 of this end shield 9 via a rolling bearing 22 in the form of a radial-axial ball bearing.
  • the inner ring 23 of the rolling bearing 22 preferably rests against a collar 24 of the motor shaft 8 while the outer ring 25 of the rolling bearing 22 preferably is supported on the other side, i.e., on the side facing the unit 2, against a locking ring 27 secured in the bearing bore hole via a pretensioned screw pressure spring 26.
  • This ring has the same supportive function as the stop ring 17 in the end shield 10.
  • the function of the spring 26 is to load the outer ring 25 of the rolling bearing 22 in an axial direction in order to eliminate the development of noise in this way. If an outer ring of a rolling bearing does not rest against anything, it tends towards swaying and thus towards noise development.
  • the force of the spring 26 must be clearly smaller than that of spring 16 to avoid cancelling the function of the latter.
  • a disk flywheel 29 preferably is fixed by a tongue and groove connection 30 in a torsionally-rigid manner on the shaft extension 28 of the motor shaft 8 on which the rolling bearing 22 is positioned.
  • the free front side of the hub 31 of the disk flywheel 29 preferably rests against the inner ring 23 of the rolling bearing 22 and preferably is axially tensioned against the inner ring 22 by a nut 33 screwed onto the threaded stem 32 of the shaft extension 28 at the same time being axially fixed in position opposite the motor shaft 8.
  • the unit comprising the rotor 7, motor shaft 8 together with rolling bearings 12, 22 and the disk flywheel 29 can therefore be moved in the direction of the central longitudinal axis 6 whereby the springs 16 and 26 positioned in the direction of shift respectively exercise a counter-force.
  • the casing 18 is closed on the side away from the motor 1 by a brake end shield 34 (brake bearing bracket) which preferably is centered vis-a-vis the casing 18 by centering collars 35 and is thus positioned coaxially to the axis 6.
  • the brake end shield 34 preferably is secured to an appropriate flange 37 of the casing by screws 36.
  • a drive shaft 38 positioned coaxially to the central longitudinal axis 6 preferably is run on bearings with full turning capacity on the one hand in a bearing bore hole 39 of the brake end shield 34, and on the other hand, in a bearing bore hole 40 in the disk flywheel 29 opposite to the latter.
  • the drive shaft 38 preferably is also run on rolling bearings 41, 42 in the form of radial-axial ball bearings in the bore holes 39, 40 respectively.
  • a coupling-brake disk 43 (clutch-brake disk) preferably is attached to the drive shaft 38 between the rolling bearings 41, 42.
  • the coupling-brake disk preferably comprises an outer armature ring 44 of magnetic material.
  • a spring washer 45 preferably is secured by screws 47 to the area of the outer edge of this armature ring 44.
  • the spring washer 45 preferably is secured to a ring collar 48 projecting radially from the drive shaft 38 by screws 47 in the area of the inside edge of the armature ring 44. This type of fixing by a thin spring washer 45 allows the armature ring 44 to move in the direction of axis 6 and coaxially thereto.
  • An annular friction pad serving as coupling facing 49 preferably is stuck to the side of the armature ring 44 facing the disk flywheel 29. This is assigned a corresponding toroid-shaped coupling surface 50 (clutch surface) on the facing front side of the disk flywheel 29.
  • the armature ring 44 preferably has a ring piece 51 on its outer perimeter protruding axially to the disk flywheel 29. This ring piece 51 preferably extends to the disk flywheel 29 with a minimal axial gap a of only a few tenths of a millimeter.
  • the outer perimeter of the annular coupling facing 49 (clutch facing) approximately rests against the inner perimeter of the ring piece 51.
  • the brake end shield 34 comprises a coupling coil casing 52 (clutch coil casing) which preferably surrounds the armature ring 44 with a minimal radial gap b of only a few tenths of a millimeter and which with a radially exterior annular casing piece 53 preferably surrounds a radial peripheral section 54 of the disk flywheel 29 adjacent to the coupling surface 50 also leaving a radial gap c of only a few tenths of a millimeter.
  • An annular electro-magnetic coupling coil 55 (clutch coil) preferably is positioned in the coupling coil casing 52 of the locally-fixed brake end shield 34.
  • the armature ring 44 preferably is equipped with a friction pad serving as brake pad 57 on the side facing away from the disk flywheel 29.
  • This brake pad preferably is also fixed by adhesion or similarly to the armature ring 44.
  • a toroid-shaped brake surface 58 has preferably been assigned to it in the brake end shield 34. While the coupling facing 49 preferably is attached to the side of the anchor ring 45 on which the spring washer 45 is secured, the annular brake pad 57 preferably is positioned in a suitably-adapted annular recess 59 of the armature ring 44.
  • the armature ring preferably made of magnetic material, extends from the recess 59 radially inwards to the proximity of the ring collar 48 which creates a toroid-shaped magnetic transmission surface 60 to the armature ring 44 which is opposite to the brake coil casing surface 61 positioned radially within the brake surface 58 and aligned therewith, preferably leaving an axial gap d of only a few tenths of a millimeter in width.
  • An annular brake coil 63 preferably is positioned in this brake coil casing 62 in such a way that, on the one hand, a magnetic flux can be transmitted radially within the brake coil 63 and radially outside the brake coil 63 but still within the brake pad 57.
  • a brake magnetic path 64 is created of which one path 64a runs radially outside the brake coil 63 through the brake coil casing 62, the axial gap d between the brake coil casing surface 61 and the magnetic transmission surface 60 --in each case between the brake pad 57 and the brake coil 63--through the armature ring (here radially towards the center) and through the axial gap d radially within the brake coil 63 back to the brake coil casing 62.
  • Another path 64b of the brake magnetic path 64 runs radially outwards into the coupling coil casing 52, through the radial gap b, and radially through the armature ring 44 towards the center where the two paths 64a and 64b meet again.
  • the coupling coil casing 52 preferably is provided with an axial-radial undercut 65 in the area of the ring piece 51 in the region facing the brake pad 57.
  • This undercut 65 preferably extends so far that the ring piece 52 extends into this undercut 65 approximately one millimeter in the direction of the brake end shield.
  • the radial and axial extension of this undercut from the nearest adjacent area of the ring piece 51 preferably is larger than 0.5 mm where even more than 1 mm is preferred so that only substantially radially-directed magnetic paths can run from the coupling coil casing 52 through the radial gap b.
  • the possibility of the ring piece 51 of the armature ring 44 "sticking" to the brake end shield 34 when the coupling coil 55 is excited is thus excluded.
  • the coupling magnetic path 56 preferably runs exclusively in substantially axial direction through the axial gap a so that the appropriate coupling power can be produced here.
  • the coupling magnetic path 56 also preferably runs exclusively substantially radially in the area of the radial gap c between the peripheral section 54 of the disk flywheel 29 and the casing piece 53 of the coupling coil casing 52 so that shifting forces can be exercised on the unit comprising rotor 7, motor shaft 8 and disk flywheel 29 which can be shifted axially against the springs 16 and 26 respectively. This is achieved through additional recesses.
  • a recess 66 preferably extends in the coupling coil casing 52 radially outwards whereby the peripheral section 54 of the disk flywheel 29 axially preferably extends into this recess 66 by about 0.5 to 1 mm.
  • the coupling coil 55 and the brake coil 63 preferably are connected in such a way that the coupling magnetic path 56 and the brake magnetic path 64b are directed against each other in the area of the coupling coil casing 52 into which both paths run. This leads to the magnetic flux being broken down more quickly and the coupling-brake disk being moved more quickly from its position at the disk flywheel 29 to position at the brake support 34 and vice-versa.
  • the air gap 68 between the coupling facing 49 and the coupling surface 50 preferably is approximately 0.1 to 0.2 mm wide, i.e., when switching from braking to coupling and vice-versa the armature ring 44 with the brake pad 57 and the coupling facing 49 has only a very short path to travel in both cases.
  • FIG. 3 shows on a larger scale the air gap 68 between the brake pad 57 and the brake surface 58 which appears during coupling.
  • the inner ring 69 of the rolling bearing 61 supported in the brake end shield preferably is supported on the side facing the disk flywheel 29 against a stop collar 70 of the drive shaft 38.
  • the outward facing side of the outer ring 71 of this rolling bearing 41 preferably abuts on an adjustment nut 72 which is screwed onto an exterior thread 73 surrounding the bearing bore hole 39 at the brake end shield 34.
  • the adjustment nut 72 preferably is secured in its position relative to the brake end shield 34 by a positioning screw 74.
  • the position of the drive shaft 38 in respect of shift movements from the brake-coupling unit 2 is fixed by the adjustment nut 72 and the above-described support of the rolling bearing 41.
  • the side of the inner ring 75 facing motor 1 is free.
  • the side of the outer ring 77 of the rolling bearing 42 facing the coupling-brake disk 43 is free.
  • the side of the outer ring 77 facing the motor 1 preferably abuts on a retaining sleeve 78 which is positioned in the bearing bore hole 40.
  • This retaining sleeve preferably has a slit 79 into which a tongue 80 of a safety plate 81 fixed by the nut 33 extends so that this retaining sleeve 78 is torsionally-rigid against the disk flywheel 29.
  • the drive shaft 38 preferably has a continuous bore hole 82 through which an adjustment screw 83 which is screwed into a threaded bore 84 in the shaft extension 28 can be turned by a screwdriver or similar tool.
  • the turning of the adjustment screw 83 in this way has the effect of adjusting the axial position of the adjustment screw or rather, in particular, the axial postion of a projecting stop collar 85 attached radially hereto relative to the motor shaft 8 and thus to the disk flywheel 29.
  • a projecting stop collar 85 attached radially hereto relative to the motor shaft 8 and thus to the disk flywheel 29.
  • One of several bimetal disks 86 which are positioned on the adjustment screw 83 preferably is supported against this stop collar 85.
  • the outer edge of the opposite disk, that is the bimetal disk nearest to the coupling-brake disk 43 preferably is supported against a ring edge 87 of the retaining sleeve 78.
  • the axial position of the disk flywheel 29 relative to the drive shaft 38 is changed by screwing the adjustment screw 83 in or out of the shaft extension 28.
  • the resting pressure force of the coupling-brake disk 43 with its brake pad 57 can be adjusted via the adjustment nut 72 against the brake area 58 of the brake end shield 34 while the air gap 68 between coupling facing 49 and the coupling surface 50 is adjusted.
  • the coupling-brake disk 43 preferably abuts on the brake surface 58 of the brake end shield 34 with initial stress, adjustable as described, when neither the coupling coil 55 nor the brake coil 63 are excited. If the coupling facing 49 and the brake pad 57 expand due to the thermal load with high alternations, this also leads to a corresponding heating of the disk flywheel 29.
  • cooling ribs 98 preferably are attached to the stator frame 3. These preferably are distributed over the area of the stator frame radially projecting and running parallel to axis 6.
  • a cup-shaped cover hood 99 enclosing the cooling ribs 98 preferably is pushed over the complete stator frame 3.
  • the floor 100 of the cover hood 99 preferably rests on spacers 101 which preferably have been cast in one piece with the end shield 10.
  • the cover hood 99 preferably is secured to these spacers 101 by screws 102.
  • the floor 100 of the cover hood 99 preferably has openings 103 through which cooling air can enter.
  • the substantially cylindrical shell 104 of the cover hood 99 preferably rests on projections 105 of the cooling ribs 98 so that these only have approximate point-wise contact to the cover hood 99.
  • a direct conduction of heat from the stator frame 3 via the cooling ribs 98 to the cover hood 99 thus only occurs to a minimal extent; the cover hood 99 is heated only minimally.
  • the cooling ribs 106 corresponding to the cooling ribs 98 preferably are also positioned in the casing 18. They preferably partially extend radially between the end shield 9 and the casing 18 since they support the end shield at the same time. There preferably is a free space 107 between the end shield 9 and the disk flywheel 29 in which the cooling channels 108 formed between the ribs 98 and the stator frame 3, or the shell 104 of the cover hood 99, or between the cooling ribs 106, the end shield 9 and the casing 18 come together.
  • suction area 109 in the disk flywheel 29 on the side facing the motor 1.
  • This suction area preferably is in the form of a ring space opening into the free space 107 which surrounds the hub 31 of the disk flywheel 29.
  • Radial channels preferably issue from this suction area 109 outwards. These are confined by radially and axially-extending ribs 111 which preferably are cast in one piece with the disk flywheel.
  • An annular-shaped air conductor ring 112 preferably is secured by screws 113 on the side of the ribs 111 facing away from the disk flywheel 29. This ring confines the radial channels 110 extending to the motor 1.
  • the fan formed in this way is an axial-radial blower.
  • the cooling air sucked through the openings flows according to the flow direction arrows 114 through the cooling channels 108, through the free space 107, the suction area 109 and through the radial channels 110. Since, as can be seen from FIG. 1, the suction area 109 extends to the proximity of the coupling surface 50, particularly efficient cooling in the critical area of the coupling surface 50 is provided.
  • the air flows from the radial channels 110 between the cooling ribs 115 which are formed on the outer perimeter and the front side of the brake end shield 34.
  • a ring-shaped sheet metal cover 117 preferably is attached to the outer front side of the brake end shield 34 by screws 116 so that a part of the air flowing between the cooling ribs 115 according to the flow arrow 118 is redirected radially inwards and cools the front side of the brake end shield.
  • the brake end shield 34 Adjacent to the brake surface 58 of the brake end shield 34 and radially between the coupling coil 55 and the brake coil 63, the brake end shield 34 preferably has an annular recess 119 serving as a turbulence chamber which extends into the proximity of the coupling coil 55, the brake coil 63 and the brake surface 58. The air is swirled in the direction of the flow arrows 118 in this chamber. It then exits through a radially inner-lying outlet 120 in the sheet metal cover 117 near the adjustment nut 72.
  • the redirection of the cooling air issuing from the radial channels 110 in radial direction into a current flowing parallel to the axis 6 between the cooling ribs 115 preferably is effected in a redirection segment 121 which is confined on the outside by the casing 18.

Landscapes

  • Engineering & Computer Science (AREA)
  • Power Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Electromagnetism (AREA)
  • Mechanical Engineering (AREA)
  • Textile Engineering (AREA)
  • Connection Of Motors, Electrical Generators, Mechanical Devices, And The Like (AREA)
  • Sewing Machines And Sewing (AREA)
  • Braking Arrangements (AREA)
  • Motor Or Generator Cooling System (AREA)
  • Control Of Electric Motors In General (AREA)
  • Control Of Direct Current Motors (AREA)
US06/836,328 1985-03-08 1986-03-05 Electromotive variable-speed and control drive particularly for use in industrial sewing machines Expired - Fee Related US4712660A (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19853508310 DE3508310A1 (de) 1985-03-08 1985-03-08 Elektromotorischer regel- und steuerantrieb, insbesondere fuer industrie-naehmaschinen
DE3508310 1985-03-08

Publications (1)

Publication Number Publication Date
US4712660A true US4712660A (en) 1987-12-15

Family

ID=6264636

Family Applications (1)

Application Number Title Priority Date Filing Date
US06/836,328 Expired - Fee Related US4712660A (en) 1985-03-08 1986-03-05 Electromotive variable-speed and control drive particularly for use in industrial sewing machines

Country Status (9)

Country Link
US (1) US4712660A (de)
EP (1) EP0196444B1 (de)
JP (1) JPS61251448A (de)
KR (1) KR860007408A (de)
AT (1) ATE52550T1 (de)
BR (1) BR8600997A (de)
DE (2) DE3508310A1 (de)
ES (1) ES292774Y (de)
PH (1) PH24011A (de)

Cited By (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5209085A (en) * 1990-02-23 1993-05-11 Hoover (Australia) Pty. Limited Clutch/brake drive unit
US5564333A (en) * 1995-10-02 1996-10-15 Palmer; Russell W. Spring biased flywheel
US5723923A (en) * 1995-02-21 1998-03-03 The United States Of America As Represented By The United States National Aeronautics And Space Administration Apparatus for providing torque and for storing momentum energy
GB2336038A (en) * 1998-04-02 1999-10-06 Brook Motors Limited Surface cooling of electrical machines
US20090090805A1 (en) * 2007-10-04 2009-04-09 Su-Yuan Hwaung Power-driven rolling and receiving apparatus
US20140291108A1 (en) * 2010-10-02 2014-10-02 Ford Global Technologies, Llc Dry-clutch transmission with cooling techniques
US8937415B2 (en) 2011-10-18 2015-01-20 Kabushiki Kaisha Yaskawa Denki Rotary electric machine having motor cover with exhaust hole in counter-load side direction
US20150226270A1 (en) * 2014-02-07 2015-08-13 Bühler Motor GmbH Electromotive drive
US9599170B1 (en) 2010-06-21 2017-03-21 Hydro-Gear Limited Partnership Electric motor clutch/brake assembly
US9866088B1 (en) 2014-09-26 2018-01-09 Hydro-Gear Limited Partnership Combination electric generator with electric clutch
CN107605988A (zh) * 2017-09-22 2018-01-19 芜湖禾丰离合器有限公司 一种减震减噪离合器

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3632064A1 (de) * 1986-09-20 1988-03-24 Frankl & Kirchner Elektromotorischer regel- und steuerantrieb
US5586635A (en) * 1995-03-31 1996-12-24 Horton, Inc. Rotational control apparatus
RU2128391C1 (ru) * 1996-07-31 1999-03-27 Орловский государственный технический университет Самовентиляционная система охлаждения торцовой электрической машины
DE19702391C1 (de) * 1997-01-24 1997-10-02 Duerkopp Adler Ag Einstellvorrichtung für eine Nähmaschine
RU2217855C2 (ru) * 2001-01-09 2003-11-27 Воронежский государственный технический университет Орбитальный роторный вентилятор
DE102015000775B4 (de) * 2015-01-26 2026-02-12 Sew-Eurodrive Gmbh & Co Kg Antrieb

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2348025A (en) * 1941-04-19 1944-05-02 Singer Mfg Co Clutch and brake mechanism
US2739251A (en) * 1952-05-01 1956-03-20 Singer Mfg Co Air cooled electric clutch-brake driving devices
US3387157A (en) * 1965-05-10 1968-06-04 Singer Co Electric motor housing in clutchbrake driving device
US3885175A (en) * 1972-12-23 1975-05-20 Frankl & Kirchner Electric motor variable speed and control drive
US3945476A (en) * 1973-04-30 1976-03-23 Quick-Rotan Becker & Notz Kg Motor construction
US4135612A (en) * 1975-11-05 1979-01-23 Frankl & Kirchner Gmbh & Co., Kg Electric motor with air cooled clutch and brake
US4556132A (en) * 1981-08-04 1985-12-03 Frankl & Kirchner Gmbh & Co. Adjustable electromagnetic clutch/brake

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1488025A1 (de) * 1963-07-31 1969-08-28 Siemens Ag Fremd- oder eingenbelueftete elektrische Maschine
DE2657658A1 (de) * 1976-12-20 1978-06-22 Quick Rotan Becker & Notz Kg Positionierantrieb
DE3027727A1 (de) * 1979-07-25 1981-02-19 Mitsubishi Electric Corp Elektromagnetische kupplung
DE3223379A1 (de) * 1981-08-04 1983-02-24 Frankl & Kirchner GmbH & Co KG Fabrik für Elektromotoren u.elektrische Apparate, 6830 Schwetzingen Elektromotorischer regel- und steuerantrieb, insbesondere fuer industrie-naehmaschinen

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2348025A (en) * 1941-04-19 1944-05-02 Singer Mfg Co Clutch and brake mechanism
US2739251A (en) * 1952-05-01 1956-03-20 Singer Mfg Co Air cooled electric clutch-brake driving devices
US3387157A (en) * 1965-05-10 1968-06-04 Singer Co Electric motor housing in clutchbrake driving device
US3885175A (en) * 1972-12-23 1975-05-20 Frankl & Kirchner Electric motor variable speed and control drive
US3945476A (en) * 1973-04-30 1976-03-23 Quick-Rotan Becker & Notz Kg Motor construction
US4135612A (en) * 1975-11-05 1979-01-23 Frankl & Kirchner Gmbh & Co., Kg Electric motor with air cooled clutch and brake
US4556132A (en) * 1981-08-04 1985-12-03 Frankl & Kirchner Gmbh & Co. Adjustable electromagnetic clutch/brake

Cited By (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5209085A (en) * 1990-02-23 1993-05-11 Hoover (Australia) Pty. Limited Clutch/brake drive unit
US5723923A (en) * 1995-02-21 1998-03-03 The United States Of America As Represented By The United States National Aeronautics And Space Administration Apparatus for providing torque and for storing momentum energy
US5564333A (en) * 1995-10-02 1996-10-15 Palmer; Russell W. Spring biased flywheel
GB2336038A (en) * 1998-04-02 1999-10-06 Brook Motors Limited Surface cooling of electrical machines
GB2336038B (en) * 1998-04-02 2002-04-24 Brook Motors Ltd Electrical machine
US20090090805A1 (en) * 2007-10-04 2009-04-09 Su-Yuan Hwaung Power-driven rolling and receiving apparatus
US7839035B2 (en) * 2007-10-04 2010-11-23 Su-Yuan Hwaung Power-driven rolling and receiving apparatus
US9599170B1 (en) 2010-06-21 2017-03-21 Hydro-Gear Limited Partnership Electric motor clutch/brake assembly
US9328776B2 (en) * 2010-10-02 2016-05-03 Ford Global Technologies, Llc Dry-clutch transmission with cooling techniques
US20140291108A1 (en) * 2010-10-02 2014-10-02 Ford Global Technologies, Llc Dry-clutch transmission with cooling techniques
US8937415B2 (en) 2011-10-18 2015-01-20 Kabushiki Kaisha Yaskawa Denki Rotary electric machine having motor cover with exhaust hole in counter-load side direction
US20150226270A1 (en) * 2014-02-07 2015-08-13 Bühler Motor GmbH Electromotive drive
US9866088B1 (en) 2014-09-26 2018-01-09 Hydro-Gear Limited Partnership Combination electric generator with electric clutch
US10530219B1 (en) 2014-09-26 2020-01-07 Hydro-Gear Limited Partnership Vehicle having combination electric generator with electric clutch
US10833560B1 (en) 2014-09-26 2020-11-10 Hydro-Gear Limited Partnership Combination electric generator with electric clutch
CN107605988A (zh) * 2017-09-22 2018-01-19 芜湖禾丰离合器有限公司 一种减震减噪离合器

Also Published As

Publication number Publication date
DE3508310A1 (de) 1986-09-18
EP0196444A1 (de) 1986-10-08
ATE52550T1 (de) 1990-05-15
BR8600997A (pt) 1986-11-18
ES292774Y (es) 1987-03-01
PH24011A (en) 1990-02-09
KR860007408A (ko) 1986-10-13
EP0196444B1 (de) 1990-05-09
JPS61251448A (ja) 1986-11-08
ES292774U (es) 1986-06-16
DE3671053D1 (de) 1990-06-13

Similar Documents

Publication Publication Date Title
US4712660A (en) Electromotive variable-speed and control drive particularly for use in industrial sewing machines
KR890001200B1 (ko) 전동 제어 구동장치
US3945476A (en) Motor construction
US4643282A (en) Motor having an electromagnetically actuated friction clutch and friction brake
US4709794A (en) Electromotive variable-speed and control drive particularly for use in industrial sewing machines
US4410819A (en) Electromagnetic coupling device
US3581855A (en) Electromagnetic clutch and brake
JPH0210291B2 (de)
EP0573079B1 (de) Kupplungsvorrichtung mit elektromagnetischem Pulver als Wirkstoff
KR19990045676A (ko) 사를 진행시키고 안내하기 위한 고데트의 베어링을 냉각시키기위한 장치 및 방법
US4172985A (en) Electric coupling and brake motor
US3063532A (en) Electromagnetic coupling with cooling means
US4598804A (en) Motor drive system
JP2005513387A (ja) 磁性粒子式制動装置
US3387157A (en) Electric motor housing in clutchbrake driving device
US4222471A (en) Clutch and brake arrangements for a motor
US4429773A (en) Electromagnetic clutch and brake
US2914156A (en) Electromagnetic clutch or brake
US4589534A (en) Electromechanical driving system with variable speed
US4550814A (en) Electromagnetic clutch-brake for industrial sewing machine
US2949991A (en) Friction clutch
CN1006161B (zh) 电动可变速及控制装置
JPH0217221Y2 (de)
CN86102500A (zh) 电动变速及控制传动装置
JPS5828460Y2 (ja) クラツチモ−タ−

Legal Events

Date Code Title Description
AS Assignment

Owner name: FRANKL & KIRCHNER GMBH & CO KG FABRIK FUR ELEKTROM

Free format text: ASSIGNMENT OF ASSIGNORS INTEREST.;ASSIGNORS:ERNDT, HANS;LINK, ERICH;MARTIN, ADOLF;AND OTHERS;REEL/FRAME:004524/0103;SIGNING DATES FROM 19860226 TO 19860227

CC Certificate of correction
FPAY Fee payment

Year of fee payment: 4

REMI Maintenance fee reminder mailed
LAPS Lapse for failure to pay maintenance fees
FP Lapsed due to failure to pay maintenance fee

Effective date: 19951220

STCH Information on status: patent discontinuation

Free format text: PATENT EXPIRED DUE TO NONPAYMENT OF MAINTENANCE FEES UNDER 37 CFR 1.362